US10184701B2 - Motor cooling and sub-cooling circuits for compressor - Google Patents

Motor cooling and sub-cooling circuits for compressor Download PDF

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US10184701B2
US10184701B2 US14/345,034 US201214345034A US10184701B2 US 10184701 B2 US10184701 B2 US 10184701B2 US 201214345034 A US201214345034 A US 201214345034A US 10184701 B2 US10184701 B2 US 10184701B2
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sub
cooling
motor
compressor
cooling fluid
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US20140345311A1 (en
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Lin Sun
Paul D. Bishop
Huai Yu Lin
Jose Alvares
Ramesh Veerasurla
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Danfoss AS
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Danfoss AS
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Assigned to DANFOSS TURBOCOR COMPRESSORS B.V. reassignment DANFOSS TURBOCOR COMPRESSORS B.V. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BISHOP, PAUL D, LIN, HUAI YU, ALVARES, Jose, SUN, LIN, VEERASURLA, Ramesh
Publication of US20140345311A1 publication Critical patent/US20140345311A1/en
Assigned to DANFOSS A/S reassignment DANFOSS A/S ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DANFOSS TURBOCOR COMPRESSORS B.V.
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/005—Compression machines, plants or systems with non-reversible cycle of the single unit type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers

Definitions

  • Refrigerant systems are known to include a main refrigerant loop in communication with a compressor, a condenser, an evaporator, and an expansion device.
  • Some compressors such as centrifugal compressors, provide motor cooling by conveying refrigerant from the main refrigerant loop to the motor.
  • An example of the disclosed refrigerant system includes a main refrigerant loop in communication with a condenser, an expansion device, an evaporator, and a compressor including at least one stage driven by a motor. Further included are motor cooling and sub-cooling lines.
  • the motor cooling line conveys motor cooling fluid between the main refrigerant loop and the motor.
  • the sub-cooling line conveys sub-cooling fluid between the main refrigerant loop and a sub-cooling heat exchanger in communication with the motor cooling line at a point upstream of the motor.
  • An example of the disclosed sub-cooling circuit includes a sub-cooling heat exchanger, and a sub-cooling line conveying a sub-cooling refrigerant between a main refrigerant loop and the sub-cooling heat exchanger.
  • the sub-cooling heat exchanger is further in communication with a motor cooling line at a point upstream of a motor.
  • An example of the disclosed motor cooling circuit includes a motor cooling line conveying a motor cooling fluid between a main refrigerant loop and a motor.
  • the motor cooling line further includes a pump to pressurize the motor cooling fluid.
  • FIG. 1A illustrates an example of the disclosed refrigerant system.
  • FIG. 1B schematically illustrates an example sub-cooling heat exchanger.
  • FIG. 1C schematically illustrates an example compressor.
  • FIGS. 1D-1E schematically illustrate example flow paths for the motor cooling fluid.
  • FIGS. 2-4 illustrate further examples of the disclosed refrigerant system.
  • the refrigerant system 10 includes a main refrigerant loop, or circuit, 12 in communication with a compressor 14 , a condenser 16 A, an evaporator 16 B, and expansion device 18 .
  • a motor cooling line 20 and a sub-cooling circuit 22 are branched from the main refrigerant loop 12 .
  • the main refrigerant loop 12 can include an economizer downstream of the condenser 16 A and upstream of the expansion device 18 .
  • the motor cooling line 20 conveys a motor cooling fluid between the main refrigerant loop 12 and the compressor 14 .
  • the motor cooling line 20 provides the motor cooling fluid to the motor of the compressor 14 as schematically illustrated in FIG. 1C , described in detail below.
  • the motor cooling line 20 includes a pump P 1 to provide pressure to the motor cooling fluid.
  • the motor cooling line 20 does not need a pump, however, and the pump P 1 could be removed altogether, or bypassed by a bypass line (e.g., bypass line 54 of the FIG. 2 embodiment).
  • the motor cooling line 20 thus can be used to provide the motor of the compressor 14 with an adequate supply of motor cooling fluid at compressor start-up, at which time there is often not enough motor cooling fluid available to the motor (and/or the associated power electronics), for example.
  • the motor cooling line 20 is effective in providing motor cooling fluid to the compressor, and for cooling the motor, in some examples it is desirable to further cool (or sub-cool) the motor cooling fluid. Accordingly, the sub-cooling circuit 22 can optionally be provided to cool the motor cooling fluid, which in turn leads to more effective, and increased, motor cooling.
  • the sub-cooling circuit 22 includes sub-cooling line 24 to convey a sub-cooling fluid between the main refrigerant loop 12 and a sub-cooling heat exchanger 26 .
  • the sub-cooling heat exchanger 26 is in communication with the motor cooling line 20 at a point upstream of the compressor 14 (i.e., upstream of the motor 40 of the compressor).
  • the sub-cooling circuit 22 further includes a sub-cooling expansion device 28 upstream of the sub-cooling heat exchanger 26 to cool the sub-cooling fluid relative to the motor cooling fluid.
  • the sub-cooling expansion device 28 need not be present, as in the examples of FIGS. 3-4 .
  • FIG. 1B An example sub-cooling heat exchanger 26 is shown in FIG. 1B .
  • the sub-cooling heat exchanger 26 is in communication with both the sub-cooling line 24 and the motor cooling line 20 .
  • the sub-cooling heat exchanger 26 includes a reservoir 30 which holds an amount of motor cooling fluid 32 at a level 34 above a point where the motor cooling line 20 enters and exits the sub-cooling heat exchanger 26 .
  • the sub-cooling line 24 includes a number of coils 36 such that heat can effectively transfer between the motor cooling fluid 32 and the sub-cooling fluid.
  • the sub-cooling heat exchanger 26 need not include a reservoir, and may be another type of heat exchanger.
  • FIG. 1C An example of the compressor 14 is schematically illustrated in FIG. 1C .
  • the compressor 14 is a centrifugal compressor having at least one stage provided by an impeller 38 that is driven by a motor 40 . While a centrifugal compressor is shown, this application extends to other compressor types.
  • the motor 40 may include a housing 40 H enclosing a rotor/stator 42 as well as motor cooling passageways 44 .
  • the housing 40 H may be a common housing, also enclosing the remainder of the compressor 14 , or may be a separate housing.
  • the motor cooling passageways 44 are fed motor cooling fluid via an opening 40 A provided by the housing 40 H.
  • a return passageway 44 A (which may be (1) an auxiliary return pipe extending outside the housing 40 H or (2) additional passageways within the housing 40 H) to direct motor cooling fluid from the motor 40 to the suction port 46 of the compressor.
  • an expansion valve 21 is positioned adjacent, and upstream, of the opening 40 A to expand the motor cooling fluid before entry into the compressor 14 .
  • this expansion valve 21 could be positioned inside the compressor 14 .
  • suction port refers to a suction header, a suction pipe, or any other component of the suction line between the expansion valve 18 and the compressor 14 .
  • this application extends to compressors with two or more compressor stages. In the example where there are two or more compressor stages, an economizer port 49 could be included between those stages, as illustrated schematically.
  • the suction port 46 of the compressor 14 can include an opening 46 A dedicated to the sub-cooling line 24 , as illustrated in FIG. 1C .
  • FIG. 1C generally illustrates the compressor 14 and the various flow paths relative thereto
  • FIGS. 1D and 1E illustrate example flow paths of the motor cooling fluid in further detail.
  • the motor cooling fluid could be guided, via the motor cooling line 20 , toward an expansion valve 21 , which may be within or outside the compressor 14 (as noted above), and then serially downstream to the motor 40 and electronics associated with the compressor 14 or the motor 40 . Then, the motor cooling fluid returns to the suction port 46 of the compressor 14 .
  • the motor 40 and the electronics could be arranged in parallel, with the motor cooling fluid branching off to separately cool these components before returning to the suction port 46 of the compressor.
  • FIG. 1A illustrates the sub-cooling circuit 22 and the motor cooling line 20 branched from the main refrigerant loop 12 at a point between the condenser 16 A and the expansion device 18
  • the motor cooling line 20 and the sub-cooling circuit 22 may be branched from the main refrigerant loop 12 at different points, as schematically illustrated across the embodiments of FIGS. 2-4 .
  • both the motor cooling line 20 and the sub-cooling circuit 24 are sourced from the condenser 16 A, and the sub-cooling circuit 24 is returned to the main refrigerant loop 12 at the evaporator 16 B.
  • the motor cooling line 20 and the sub-cooling circuit 24 are each in communication with a plurality of valves 50 A- 50 D.
  • these valves 50 A- 50 D could be check valves, or any other appropriate type of valve.
  • the motor cooling line 20 could be sourced from the evaporator 16 B instead of the condenser 16 A (e.g., by operating pump P 2 and not P 1 ), and the sub-cooling circuit 24 could be returned to the compressor 14 via the opening of the valve 50 D.
  • These alternate paths are shown in phantom in FIG. 2 .
  • valves 50 A- 50 D are solenoid valves
  • the valves 50 A- 50 D may be in communication with a controller 52 , either wirelessly or otherwise, which controls opening and closing of the valves 50 A- 50 D.
  • the pump P 1 of the motor cooling line 20 is arranged in parallel with a bypass line 54 , including a solenoid valve 56 A. If the pump P 1 is not needed to provide added pressure to the motor cooling fluid, then the solenoid valve 56 A may be opened, allowing the motor cooling fluid to bypass the pump P 1 . Operation of the solenoid valve 56 A may be controlled by the controller 52 .
  • the pump P 2 may be used to provide added pressure to the motor cooling fluid. While not illustrated, the pump P 2 could be arranged in parallel with a bypass line (similar to bypass line 54 ).
  • the sub-cooling circuit 24 is sourced from the evaporator 16 B.
  • the sub-cooling circuit 24 includes a pump P 3 upstream of the sub-cooling heat exchanger 26 to provide additional pressure to the sub-cooling fluid. While not illustrated, the pump P 3 could be bypassed.
  • the sub-cooling circuit 22 is returned to the main refrigerant loop 12 at the compressor 14 , by way of the arrangement of the valves 50 C- 50 D.
  • the sub-cooling circuit 22 may be returned to the opening 46 A illustrated in FIG. 1C .
  • the sub-cooling circuit 22 could be returned upstream of the suction port 46 of the compressor, or to the economizer port 49 (if present).
  • the portion of the sub-cooling circuit 22 downstream of the valve 50 D is representative, generally, of the sub-cooling circuit 22 being in connection with an economizer port.
  • the sub-cooling circuit need not include a sub-cooling expansion device 28 upstream of the sub-cooling heat exchanger 26 . This is due to the nature of the fluid tapped from the evaporator 16 B, which is already sufficiently cool (relative to the motor cooling fluid). An expansion device can be included if desired, however.
  • FIG. 4 illustrates an embodiment in which the sub-cooling circuit 24 is sourced from, and returns to, the compressor 14 .
  • the compressor 14 may house an internal fluid line 12 A (shown schematically, and in phantom, in FIG. 1C ) in communication with an internal expansion device 12 B.
  • the internal fluid line 12 A may be located within a housing of the compressor 14 .
  • the internal fluid line 12 A is the source of the sub-cooling circuit 24 .
  • the sub-cooling circuit 24 may be in communication with one or more solenoid valves 56 B- 56 C controlled by the controller 52 to meter the flow of sub-cooling fluid between the sub-cooling heating exchanger 26 and the compressor 14 .
  • the branch of the sub-cooling circuit associated with the solenoid valve 56 C may be utilized to cool electronics associated with the compressor 14 .
  • the sub-cooling circuit 24 can be source from an economizer, in the example where the main refrigerant loop 12 includes an economizer.
  • the sub-cooling circuit 24 can be returned to either of the evaporator 16 B, the suction port 46 of the compressor, or the economizer port 49 of the compressor.
  • the sub-cooling and motor cooling fluid may be a refrigerant, such as R-134a, and may be primarily in a liquid state when initially tapped from the main refrigerant loop 12 .
  • This application is not limited to R-134a, however, and could include any other type of refrigerant.
  • the tapping and returning of the sub-cooling and motor cooling fluid to the main refrigerant loop 12 may be done in any known manner to maximize the overall efficiency of the refrigerant system 10 .
  • the sub-cooling circuit 22 in the above examples has been discussed as being primarily useful for cooling the motor cooling line 20 , the sub-cooling circuit 22 may optionally, or additionally, be used to provide cooling to other components in the refrigerant system 10 .
  • the sub-cooling circuit 22 may be routed, or may include a separate branch, to cool electronics associated with the compressor 14 (as illustrated in FIGS. 1D-1E ), and/or to cool the controller 52 .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
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Abstract

The disclosed refrigerant system includes a compressor having a motor that is cooled by motor cooling fluid provided to the motor from the main refrigerant loop by a motor cooling circuit. The system also includes a sub-cooling circuit to cool the motor cooling fluid.

Description

RELATED APPLICATIONS
This application claims the benefit of U.S. Provisional Application No. 61/535,566, filed 16 Sep. 2011.
BACKGROUND
Refrigerant systems are known to include a main refrigerant loop in communication with a compressor, a condenser, an evaporator, and an expansion device. Some compressors, such as centrifugal compressors, provide motor cooling by conveying refrigerant from the main refrigerant loop to the motor.
SUMMARY
An example of the disclosed refrigerant system includes a main refrigerant loop in communication with a condenser, an expansion device, an evaporator, and a compressor including at least one stage driven by a motor. Further included are motor cooling and sub-cooling lines. The motor cooling line conveys motor cooling fluid between the main refrigerant loop and the motor. The sub-cooling line conveys sub-cooling fluid between the main refrigerant loop and a sub-cooling heat exchanger in communication with the motor cooling line at a point upstream of the motor.
An example of the disclosed sub-cooling circuit includes a sub-cooling heat exchanger, and a sub-cooling line conveying a sub-cooling refrigerant between a main refrigerant loop and the sub-cooling heat exchanger. The sub-cooling heat exchanger is further in communication with a motor cooling line at a point upstream of a motor.
An example of the disclosed motor cooling circuit includes a motor cooling line conveying a motor cooling fluid between a main refrigerant loop and a motor. The motor cooling line further includes a pump to pressurize the motor cooling fluid.
These and other features of the present disclosure can be best understood from the following drawings and detailed description.
BRIEF DESCRIPTION OF THE DRAWINGS
The drawings can be briefly described as follows:
FIG. 1A illustrates an example of the disclosed refrigerant system.
FIG. 1B schematically illustrates an example sub-cooling heat exchanger.
FIG. 1C schematically illustrates an example compressor.
FIGS. 1D-1E schematically illustrate example flow paths for the motor cooling fluid.
FIGS. 2-4 illustrate further examples of the disclosed refrigerant system.
 DETAILED DESCRIPTION
With reference to FIG. 1A, an example of the disclosed refrigerant system 10 is illustrated. The refrigerant system 10 includes a main refrigerant loop, or circuit, 12 in communication with a compressor 14, a condenser 16A, an evaporator 16B, and expansion device 18. A motor cooling line 20 and a sub-cooling circuit 22 are branched from the main refrigerant loop 12. Notably, while a particular example of the refrigerant system 10 is shown, this application extends to other refrigerant system configurations. For instance, the main refrigerant loop 12 can include an economizer downstream of the condenser 16A and upstream of the expansion device 18.
The motor cooling line 20 conveys a motor cooling fluid between the main refrigerant loop 12 and the compressor 14. In particular, the motor cooling line 20 provides the motor cooling fluid to the motor of the compressor 14 as schematically illustrated in FIG. 1C, described in detail below. The motor cooling line 20 includes a pump P1 to provide pressure to the motor cooling fluid. The motor cooling line 20 does not need a pump, however, and the pump P1 could be removed altogether, or bypassed by a bypass line (e.g., bypass line 54 of the FIG. 2 embodiment). The motor cooling line 20 thus can be used to provide the motor of the compressor 14 with an adequate supply of motor cooling fluid at compressor start-up, at which time there is often not enough motor cooling fluid available to the motor (and/or the associated power electronics), for example.
While the motor cooling line 20, alone, is effective in providing motor cooling fluid to the compressor, and for cooling the motor, in some examples it is desirable to further cool (or sub-cool) the motor cooling fluid. Accordingly, the sub-cooling circuit 22 can optionally be provided to cool the motor cooling fluid, which in turn leads to more effective, and increased, motor cooling.
The sub-cooling circuit 22 includes sub-cooling line 24 to convey a sub-cooling fluid between the main refrigerant loop 12 and a sub-cooling heat exchanger 26. The sub-cooling heat exchanger 26 is in communication with the motor cooling line 20 at a point upstream of the compressor 14 (i.e., upstream of the motor 40 of the compressor). In this example, the sub-cooling circuit 22 further includes a sub-cooling expansion device 28 upstream of the sub-cooling heat exchanger 26 to cool the sub-cooling fluid relative to the motor cooling fluid. The sub-cooling expansion device 28 need not be present, as in the examples of FIGS. 3-4.
An example sub-cooling heat exchanger 26 is shown in FIG. 1B. As illustrated, the sub-cooling heat exchanger 26 is in communication with both the sub-cooling line 24 and the motor cooling line 20. In the example, the sub-cooling heat exchanger 26 includes a reservoir 30 which holds an amount of motor cooling fluid 32 at a level 34 above a point where the motor cooling line 20 enters and exits the sub-cooling heat exchanger 26. The sub-cooling line 24 includes a number of coils 36 such that heat can effectively transfer between the motor cooling fluid 32 and the sub-cooling fluid. Notably, the sub-cooling heat exchanger 26 need not include a reservoir, and may be another type of heat exchanger.
An example of the compressor 14 is schematically illustrated in FIG. 1C. In this example, the compressor 14 is a centrifugal compressor having at least one stage provided by an impeller 38 that is driven by a motor 40. While a centrifugal compressor is shown, this application extends to other compressor types.
The motor 40 may include a housing 40H enclosing a rotor/stator 42 as well as motor cooling passageways 44. The housing 40H may be a common housing, also enclosing the remainder of the compressor 14, or may be a separate housing. The motor cooling passageways 44 are fed motor cooling fluid via an opening 40A provided by the housing 40H. Further included is a return passageway 44A (which may be (1) an auxiliary return pipe extending outside the housing 40H or (2) additional passageways within the housing 40H) to direct motor cooling fluid from the motor 40 to the suction port 46 of the compressor. Notably, an expansion valve 21 is positioned adjacent, and upstream, of the opening 40A to expand the motor cooling fluid before entry into the compressor 14. Alternatively, this expansion valve 21 could be positioned inside the compressor 14.
As the motor 40 drives the impeller 38, refrigerant from the main refrigerant loop 12 is drawn into a suction port, or inlet, 46 and is outlet from the compressor back to the main refrigerant loop 12 via an outlet 48. For purposes of this disclosure, “suction port” refers to a suction header, a suction pipe, or any other component of the suction line between the expansion valve 18 and the compressor 14. Notably, while only one impeller 38 is shown, this application extends to compressors with two or more compressor stages. In the example where there are two or more compressor stages, an economizer port 49 could be included between those stages, as illustrated schematically.
While the sub-cooling circuit 22 is shown returning to the main refrigerant loop 12 at a point upstream of the suction port 46 of the compressor (as shown in FIG. 1A), the suction port 46 of the compressor 14 can include an opening 46A dedicated to the sub-cooling line 24, as illustrated in FIG. 1C.
While FIG. 1C generally illustrates the compressor 14 and the various flow paths relative thereto, FIGS. 1D and 1E illustrate example flow paths of the motor cooling fluid in further detail. Referring to FIG. 1D, the motor cooling fluid could be guided, via the motor cooling line 20, toward an expansion valve 21, which may be within or outside the compressor 14 (as noted above), and then serially downstream to the motor 40 and electronics associated with the compressor 14 or the motor 40. Then, the motor cooling fluid returns to the suction port 46 of the compressor 14. Alternatively, as illustrated in FIG. 1E, the motor 40 and the electronics could be arranged in parallel, with the motor cooling fluid branching off to separately cool these components before returning to the suction port 46 of the compressor.
Whereas the example of FIG. 1A illustrates the sub-cooling circuit 22 and the motor cooling line 20 branched from the main refrigerant loop 12 at a point between the condenser 16A and the expansion device 18, the motor cooling line 20 and the sub-cooling circuit 22 may be branched from the main refrigerant loop 12 at different points, as schematically illustrated across the embodiments of FIGS. 2-4.
In the embodiment of FIG. 2, both the motor cooling line 20 and the sub-cooling circuit 24 are sourced from the condenser 16A, and the sub-cooling circuit 24 is returned to the main refrigerant loop 12 at the evaporator 16B.
The motor cooling line 20 and the sub-cooling circuit 24 are each in communication with a plurality of valves 50A-50D. Notably, while solenoid valves are shown, these valves 50A-50D could be check valves, or any other appropriate type of valve. Depending on which pump P1, P2 is active, the motor cooling line 20 could be sourced from the evaporator 16B instead of the condenser 16A (e.g., by operating pump P2 and not P1), and the sub-cooling circuit 24 could be returned to the compressor 14 via the opening of the valve 50D. These alternate paths are shown in phantom in FIG. 2.
In the example where the valves 50A-50D are solenoid valves, the valves 50A-50D may be in communication with a controller 52, either wirelessly or otherwise, which controls opening and closing of the valves 50A-50D. Notably, the pump P1 of the motor cooling line 20 is arranged in parallel with a bypass line 54, including a solenoid valve 56A. If the pump P1 is not needed to provide added pressure to the motor cooling fluid, then the solenoid valve 56A may be opened, allowing the motor cooling fluid to bypass the pump P1. Operation of the solenoid valve 56A may be controlled by the controller 52. Notably, if the motor cooling line 24 is sourced from the evaporator 16B, the pump P2 may be used to provide added pressure to the motor cooling fluid. While not illustrated, the pump P2 could be arranged in parallel with a bypass line (similar to bypass line 54).
In the example of FIG. 3, the sub-cooling circuit 24 is sourced from the evaporator 16B. In this example, the sub-cooling circuit 24 includes a pump P3 upstream of the sub-cooling heat exchanger 26 to provide additional pressure to the sub-cooling fluid. While not illustrated, the pump P3 could be bypassed. Notably, the sub-cooling circuit 22 is returned to the main refrigerant loop 12 at the compressor 14, by way of the arrangement of the valves 50C-50D. In particular, the sub-cooling circuit 22 may be returned to the opening 46A illustrated in FIG. 1C. As additional examples, the sub-cooling circuit 22 could be returned upstream of the suction port 46 of the compressor, or to the economizer port 49 (if present). The portion of the sub-cooling circuit 22 downstream of the valve 50D is representative, generally, of the sub-cooling circuit 22 being in connection with an economizer port.
Notably, in the example of FIG. 3, the sub-cooling circuit need not include a sub-cooling expansion device 28 upstream of the sub-cooling heat exchanger 26. This is due to the nature of the fluid tapped from the evaporator 16B, which is already sufficiently cool (relative to the motor cooling fluid). An expansion device can be included if desired, however.
FIG. 4 illustrates an embodiment in which the sub-cooling circuit 24 is sourced from, and returns to, the compressor 14. The compressor 14 may house an internal fluid line 12A (shown schematically, and in phantom, in FIG. 1C) in communication with an internal expansion device 12B. The internal fluid line 12A may be located within a housing of the compressor 14.
In this example, the internal fluid line 12A is the source of the sub-cooling circuit 24. The sub-cooling circuit 24 may be in communication with one or more solenoid valves 56B-56C controlled by the controller 52 to meter the flow of sub-cooling fluid between the sub-cooling heating exchanger 26 and the compressor 14. Notably, the branch of the sub-cooling circuit associated with the solenoid valve 56C may be utilized to cool electronics associated with the compressor 14.
While the Figures illustrate various example sources for the sub-cooling circuit 24, it is further possible to source the sub-cooling circuit from an economizer, in the example where the main refrigerant loop 12 includes an economizer. In this example, the sub-cooling circuit 24 can be returned to either of the evaporator 16B, the suction port 46 of the compressor, or the economizer port 49 of the compressor.
It should be understood that the sub-cooling and motor cooling fluid may be a refrigerant, such as R-134a, and may be primarily in a liquid state when initially tapped from the main refrigerant loop 12. This application is not limited to R-134a, however, and could include any other type of refrigerant. Further, the tapping and returning of the sub-cooling and motor cooling fluid to the main refrigerant loop 12 may be done in any known manner to maximize the overall efficiency of the refrigerant system 10.
While the sub-cooling circuit 22 in the above examples has been discussed as being primarily useful for cooling the motor cooling line 20, the sub-cooling circuit 22 may optionally, or additionally, be used to provide cooling to other components in the refrigerant system 10. For example, the sub-cooling circuit 22 may be routed, or may include a separate branch, to cool electronics associated with the compressor 14 (as illustrated in FIGS. 1D-1E), and/or to cool the controller 52.
Although the different examples have the specific components shown in the illustrations, embodiments of this invention are not limited to those particular combinations. It is possible to use some of the components or features from one of the examples in combination with features or components from another one of the examples.
One of ordinary skill in this art would understand that the above-described embodiments are exemplary and non-limiting. That is, modifications of this disclosure would come within the scope of the claims. Accordingly, the following claims should be studied to determine their true scope and content.

Claims (16)

What is claimed is:
1. A refrigerant system, comprising:
a main refrigerant loop in communication with a condenser, an expansion device, an evaporator, and a compressor driven by a motor;
a motor cooling line to convey a motor cooling fluid between the main refrigerant loop and the motor; and
a sub-cooling line to convey a sub-cooling fluid between the main refrigerant loop and a sub-cooling heat exchanger, the sub-cooling heat exchanger in communication with the motor cooling line at a point upstream of the motor, and wherein the motor cooling line includes a pump upstream of the sub-cooling heat exchanger.
2. The refrigerant system as recited in claim 1, wherein the motor cooling fluid is cooled at the sub-cooling heat exchanger.
3. The refrigerant system as recited in claim 1, wherein the sub-cooling fluid is sourced from the condenser, and wherein the sub-cooling fluid is returned to the main refrigerant loop at one of the evaporator, a suction port of the compressor, and an economizer port of the compressor.
4. The refrigerant system as recited in claim 3, wherein the sub-cooling line includes a sub-cooling expansion device upstream of the sub-cooling heat exchanger.
5. The refrigerant system as recited in claim 1, wherein the sub-cooling fluid is sourced from the evaporator, and wherein the sub-cooling fluid is returned to the main refrigerant loop at one of the evaporator, a suction port of the compressor, and an economizer port of the compressor.
6. The refrigerant system as recited in claim 5, wherein the sub-cooling line includes a pump upstream of the sub-cooling heat exchanger.
7. The refrigerant system as recited in claim 1, wherein the sub-cooling fluid is sourced directly from the compressor, and wherein the sub-cooling fluid is returned to the main refrigerant line at a suction port of the compressor.
8. The refrigerant system as recited in claim 1, wherein the sub-cooling fluid is sourced from an economizer, and wherein the sub-cooling fluid is returned to the main refrigerant loop at one of the evaporator, a suction port of the compressor, and an economizer port of the compressor.
9. The refrigerant system as recited in claim 1, wherein the motor cooling fluid is sourced from one of the condenser and the evaporator.
10. The refrigerant system as recited in claim 1, wherein the motor cooling line is in communication with a reservoir, the reservoir configured to store an amount of motor cooling fluid.
11. The refrigerant system as recited in claim 1, wherein the motor cooling line includes a bypass line arranged in parallel with the pump.
12. The refrigerant system as recited in claim 11, wherein the bypass line includes a flow regulator configured to selectively allow fluid to bypass the pump.
13. A system, comprising:
a motor cooling line conveying a motor cooling fluid between a main refrigerant loop and a motor, wherein the motor cooling line includes a pump to pressurize the motor cooling fluid; and
a sub-cooling line to convey a sub-cooling fluid between the main refrigerant loop and a sub-cooling heat exchanger, the sub-cooling heat exchanger in communication with the motor cooling line at a point upstream of the motor, wherein the pump of the motor cooling line is upstream of the sub-cooling heat exchanger.
14. The system as recited in claim 13, wherein the motor cooling fluid is sourced from one of a condenser and an evaporator.
15. The system as recited in claim 13, wherein the motor cooling fluid is sourced at a point downstream of a condenser and upstream of an expansion valve.
16. The system as recited in claim 13, wherein the motor cooling line includes a bypass line having a solenoid valve, the bypass line arranged in parallel with the pump, the solenoid valve configured to selectively allow fluid to bypass the pump.
US14/345,034 2011-09-16 2012-05-08 Motor cooling and sub-cooling circuits for compressor Active 2035-02-04 US10184701B2 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11988421B2 (en) 2021-05-20 2024-05-21 Carrier Corporation Heat exchanger for power electronics

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150300708A1 (en) * 2012-11-29 2015-10-22 Keltech Inc. Cooling system and method for magnetic bearing compressors
US9671146B2 (en) 2013-01-25 2017-06-06 Trane International Inc. Refrigerant cooling and lubrication system with refrigerant vapor vent line
JP6141526B2 (en) * 2013-10-09 2017-06-07 ジョンソン コントロールズ テクノロジー カンパニーＪｏｈｎｓｏｎ Ｃｏｎｔｒｏｌｓ Ｔｅｃｈｎｏｌｏｇｙ Ｃｏｍｐａｎｙ Motor housing temperature control system
WO2016003467A1 (en) * 2014-07-03 2016-01-07 Danfoss A/S Refrigerant cooling for variable speed drive
EP3280892A4 (en) * 2015-04-07 2018-03-21 Conoco Phillips Company Quench system for a refrigeration cycle of a liquefied natural gas facility and method of quenching
CN105329065B (en) * 2015-11-20 2017-05-31 浙江华晨动力机械有限公司 The air-conditioning system of Electric Transit bus
US11187447B2 (en) * 2016-01-27 2021-11-30 Mitsubishi Electric Corporation Refrigeration cycle apparatus
CN105783136B (en) * 2016-04-14 2019-04-02 海信（山东）空调有限公司 A kind of outdoor air-conditioner and air-conditioning system
CN106642778A (en) * 2016-11-14 2017-05-10 重庆美的通用制冷设备有限公司 Oilless water chilling unit and air conditioning system
US11022355B2 (en) 2017-03-24 2021-06-01 Johnson Controls Technology Company Converging suction line for compressor
EP3688314A2 (en) 2017-09-25 2020-08-05 Johnson Controls Technology Company Two piece split scroll for centrifugal compressor
JP7265540B2 (en) 2017-09-25 2023-04-26 ジョンソン コントロールズ テクノロジー カンパニー Input current control for variable speed drives
CN111373155B (en) 2017-09-25 2022-09-02 江森自控科技公司 Compact variable geometry diffuser mechanism
WO2019060752A1 (en) 2017-09-25 2019-03-28 Johnson Controls Technology Company Two step oil motive eductor system
US11156231B2 (en) 2018-03-23 2021-10-26 Honeywell International Inc. Multistage compressor having interstage refrigerant path split between first portion flowing to end of shaft and second portion following around thrust bearing disc
US20210247107A1 (en) * 2018-10-03 2021-08-12 Carrier Corporation Method and system for cooling a motor during motor startup
CN109556256A (en) * 2018-10-17 2019-04-02 青岛海尔空调电子有限公司 Air conditioner
CN111365897A (en) * 2018-12-26 2020-07-03 珠海格力电器股份有限公司 Motor cooling loop of compressor, cooling method, refrigerating system and air conditioner
DE102019203181A1 (en) * 2019-03-08 2020-09-10 Denso Automotive Deutschland Gmbh Compact chiller
EP3742077B1 (en) * 2019-05-21 2023-08-16 Carrier Corporation Refrigeration apparatus and use thereof
CN112747391A (en) * 2019-10-29 2021-05-04 青岛海尔空调电子有限公司 Air conditioning unit and compressor cooling control method thereof
CN113324312B (en) * 2020-02-28 2022-10-28 青岛海尔空调电子有限公司 Control method of air conditioning unit and air conditioning unit
US12050036B2 (en) * 2020-04-30 2024-07-30 Danfoss A/S System and method for cooling power electronics of refrigerant compressors

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1473086A (en) 1973-06-28 1977-05-11
JPH02287058A (en) 1989-04-26 1990-11-27 Daikin Ind Ltd Screw type refrigerator
DE4122889C1 (en) 1991-07-11 1992-12-17 Bitzer Kuehlmaschinenbau Gmbh & Co Kg, 7032 Sindelfingen, De
US5806327A (en) 1996-06-28 1998-09-15 Lord; Richard G. Compressor capacity reduction
US5884498A (en) 1996-10-25 1999-03-23 Mitsubishi Heavy Industries, Ltd. Turborefrigerator
US6182467B1 (en) * 1999-09-27 2001-02-06 Carrier Corporation Lubrication system for screw compressors using an oil still
US6324858B1 (en) * 1998-11-27 2001-12-04 Carrier Corporation Motor temperature control
US6651451B2 (en) 2002-04-23 2003-11-25 Vai Holdings, Llc Variable capacity refrigeration system with a single-frequency compressor
US20070256432A1 (en) 2002-12-09 2007-11-08 Kevin Zugibe Method and apparatus for optimizing refrigeration systems
US20090025405A1 (en) 2007-07-27 2009-01-29 Johnson Controls Technology Company Economized Vapor Compression Circuit
JP2011047535A (en) 2009-08-25 2011-03-10 Kobe Steel Ltd Refrigerating device
US20110132007A1 (en) 2008-09-26 2011-06-09 Carrier Corporation Compressor discharge control on a transport refrigeration system

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6434960B1 (en) * 2001-07-02 2002-08-20 Carrier Corporation Variable speed drive chiller system
CN1745282B (en) * 2002-12-09 2010-04-21 哈德逊技术公司 Method and apparatus for optimizing refrigeration systems
US8021127B2 (en) * 2004-06-29 2011-09-20 Johnson Controls Technology Company System and method for cooling a compressor motor
JP5197141B2 (en) * 2008-05-12 2013-05-15 株式会社神戸製鋼所 Two-stage screw compressor and refrigeration system
US20120255318A1 (en) * 2009-12-22 2012-10-11 Naohiro Kido Refrigeration apparatus

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1473086A (en) 1973-06-28 1977-05-11
JPH02287058A (en) 1989-04-26 1990-11-27 Daikin Ind Ltd Screw type refrigerator
DE4122889C1 (en) 1991-07-11 1992-12-17 Bitzer Kuehlmaschinenbau Gmbh & Co Kg, 7032 Sindelfingen, De
US5806327A (en) 1996-06-28 1998-09-15 Lord; Richard G. Compressor capacity reduction
US5884498A (en) 1996-10-25 1999-03-23 Mitsubishi Heavy Industries, Ltd. Turborefrigerator
US6324858B1 (en) * 1998-11-27 2001-12-04 Carrier Corporation Motor temperature control
US6182467B1 (en) * 1999-09-27 2001-02-06 Carrier Corporation Lubrication system for screw compressors using an oil still
US6651451B2 (en) 2002-04-23 2003-11-25 Vai Holdings, Llc Variable capacity refrigeration system with a single-frequency compressor
US20070256432A1 (en) 2002-12-09 2007-11-08 Kevin Zugibe Method and apparatus for optimizing refrigeration systems
US20090025405A1 (en) 2007-07-27 2009-01-29 Johnson Controls Technology Company Economized Vapor Compression Circuit
US20110132007A1 (en) 2008-09-26 2011-06-09 Carrier Corporation Compressor discharge control on a transport refrigeration system
JP2011047535A (en) 2009-08-25 2011-03-10 Kobe Steel Ltd Refrigerating device

Non-Patent Citations (3)

* Cited by examiner, † Cited by third party
Title
International Preliminary Report for International Application No. PCT/US2012/036868 dated Mar. 27, 2014.
International Search Report and Written Opinion dated Jul. 18, 2012.
Supplementary European Search Report for European Patent Application No. 12832508.1 dated Sep. 15, 2015.

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11988421B2 (en) 2021-05-20 2024-05-21 Carrier Corporation Heat exchanger for power electronics

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CN103782117B (en) 2016-05-18
WO2013039572A1 (en) 2013-03-21

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